A heat engine working fluid compressor performance testing system and method

Abstract

The application discloses a heat engine working medium compressor performance test system and method, which comprises a total control module, a working medium control module, a heat engine working medium compressor and a driving module; wherein the total control module is connected with the rest modules respectively, is used for controlling the working state of each module, and collects real-time data; the working medium control module is used for receiving high-pressure working medium compressed by the heat engine working medium compressor, and inputting low-pressure working medium to the heat engine working medium compressor; the heat engine working medium compressor is used for pressurizing the working medium in the low-pressure working medium bottle and making the working medium enter the high-pressure working medium bottle; the driving module is used for providing power for the compression cycle of the heat engine working medium compressor, and is also used for measuring the rotating speed and torque of the heat engine working medium compressor. When the performance test is performed, the total control module controls the opening or closing of an exhaust electromagnetic valve, an intake electromagnetic valve and a short-circuit electromagnetic valve. The maximum torque of the working medium compressor is measured, the power consumption is calculated, and whether the performance test is qualified is judged.

Description

Technical Field

[0001] This application relates to the field of mechanical performance testing, and more specifically, to a performance testing system and method for a hot gas engine working fluid compressor. Background Technology

[0002] A hot air compressor uses a working gas to drive a piston, offering advantages such as simple structure, low vibration and noise, and strong adaptability. In hot air compressor power generation applications, working gas pressure regulation is one of the technical means of power control. When the power output increases, the working gas pressure needs to be increased; conversely, when the power output decreases, the working gas pressure needs to be decreased. When the working gas pressure is reduced, the working gas needs to be discharged. To improve the economic efficiency of hot air compressor applications, the discharged working gas needs to be recycled. However, the pressure of the discharged working gas is too low to directly enter the high-pressure working gas cylinder. This necessitates the use of a hot air compressor working gas compressor. The hot air compressor crankshaft drives the compressor connecting rod, which in turn drives the compressor piston assembly in a reciprocating motion, converting the low-pressure working gas discharged from the hot air compressor into a high-pressure working gas—that is, pressurizing it—before it enters the high-pressure working gas cylinder for use by the hot air compressor, thus achieving the working gas recycling function. However, using a substandard working fluid compressor in a hot air engine will seriously affect the reliability of the hot air engine. Therefore, a performance testing module and method for hot air engine working fluid compressors is needed to test the performance of the working fluid compressors and select qualified working fluid compressors for use in hot air engines, so as to improve the reliability of hot air engines. Summary of the Invention

[0003] To address the aforementioned technical problems, this application provides a performance testing system and method for a hot gas engine working fluid compressor. By conducting power consumption performance tests and pressure ratio performance tests on the hot gas engine working fluid compressor, qualified hot gas engine working fluid compressors are selected for application.

[0004] Specifically, the technical solution of this application is as follows:

[0005] In a first aspect, this application discloses a performance testing system for a hot gas engine working fluid compressor, comprising: a main control module, a working fluid control module, a hot gas engine working fluid compressor, a drive module, a cooling module, and an oil module;

[0006] The working fluid control module is connected to the hot gas engine working fluid compressor and is used to receive the high-pressure working fluid after being compressed by the hot gas engine working fluid compressor, and to input the low-pressure working fluid into the hot gas engine working fluid compressor; it includes an exhaust solenoid valve, a high-pressure working fluid bottle, an overflow valve, a low-pressure working fluid bottle, and an intake solenoid valve connected in sequence; it also includes a short-circuit solenoid valve, a first pressure sensor, and a second pressure sensor.

[0007] One end of the first pressure sensor is connected to the branch line connecting the high-pressure working fluid bottle and the overflow valve; the first pressure sensor is used to measure the exhaust pressure of the hot gas engine working fluid compressor;

[0008] One end of the second pressure sensor is connected to the branch line where the intake solenoid valve connects to the intake port; the second pressure sensor is used to measure the intake pressure of the working fluid compressor of the hot air engine;

[0009] The hot air compressor is used to pressurize the working fluid in the low-pressure working fluid bottle and send it into the high-pressure working fluid bottle; it includes an air inlet and an air outlet, the air inlet being connected to the air inlet solenoid valve; the air outlet being connected to the air outlet solenoid valve.

[0010] The drive module is connected to the hot gas compressor and is used to provide power for the compression cycle of the hot gas compressor. The drive module includes a torque measuring instrument, which is used to measure the speed and torque of the hot gas compressor.

[0011] The main control module is connected to the other modules and is used to control the working status of each module. According to the preset sampling period, it collects real-time data of each module in each sampling period and sends the real-time data to the background. The real-time data includes: the exhaust pressure measured by the first pressure sensor, the intake pressure obtained by the second pressure sensor, and the speed and torque measured by the torque measuring instrument.

[0012] The main control module is also used to control the working time and related working parameters of the exhaust solenoid valve, the intake solenoid valve, the short-circuit solenoid valve and the drive module;

[0013] The main control module is also used to control the short-circuit solenoid valve to be in the open state when the hot gas engine working fluid compressor is subjected to the first performance test; and to control the short-circuit solenoid valve to be in the closed state when the hot gas engine working fluid compressor is subjected to the second performance test; the main control module is also used to calculate the maximum power consumption of the hot gas engine working fluid compressor during the test.

[0014] The cooling module is used to cool and dissipate heat from the working fluid compressor of the hot gas engine;

[0015] The oil module is used to lubricate the working fluid compressor of the hot air engine.

[0016] Secondly, this application also discloses a performance testing method for a hot gas engine working fluid compressor, characterized in that the method for testing the performance of the hot gas engine working fluid compressor described in any of the above embodiments includes the following steps:

[0017] A first performance test is performed on the hot gas compressor: the short-circuit solenoid valve is opened, and the hot gas compressor is started to run for a first duration under a first intake pressure and a first speed; the first maximum torque of the hot gas compressor during the first performance test is obtained, and the first maximum power consumption of the hot gas compressor is calculated; if the first maximum power consumption is less than the first target power consumption, the first performance test of the hot gas compressor is qualified.

[0018] A second performance test is performed on the hot gas compressor: the short-circuit solenoid valve is closed, and the hot gas compressor is operated under the second inlet pressure and the second speed. The second time taken for the pressure ratio of the hot gas compressor to increase from 1 to the target pressure ratio during the second performance test is calculated. The second maximum torque of the hot gas compressor during the second performance test is obtained, and the second maximum power consumption of the hot gas compressor is calculated. If the second maximum power consumption is less than the second target power consumption and the second time is less than the second target time, then the second performance test of the hot gas compressor is qualified.

[0019] In some embodiments, obtaining the first maximum torque of the hot gas engine working fluid compressor during the first performance test, and thereby calculating the first maximum power consumption of the hot gas engine working fluid compressor, specifically includes the following steps:

[0020] Multiple torques measured by a torque measuring instrument during the first performance test are obtained, and the torque with the largest value among the multiple torques is selected as the first maximum torque;

[0021] The first maximum power consumption W1 of the working fluid compressor of the hot gas engine is calculated using the following formula:

[0022]

[0023] Where a is a constant; T1 is the first duration; M max1 N1 is the first maximum torque; N2 is the first rotational speed.

[0024] In some implementations, the following steps are also included:

[0025] The pressure of the high-pressure working fluid bottle, i.e., the exhaust pressure, is measured by the first pressure sensor; the pressure of the low-pressure working fluid bottle, i.e., the intake pressure, is measured by the second pressure sensor.

[0026] The pressure ratio is equal to the exhaust pressure divided by the intake pressure.

[0027] In some embodiments, the second time taken to increase the pressure ratio of the hot gas engine working fluid compressor from 1 to the target pressure ratio during the second performance test specifically includes the following steps:

[0028] The exhaust solenoid valve and the intake solenoid valve are opened to control the exhaust pressure and the intake pressure to be the same, both being the second intake pressure; the drive module is controlled to drive the hot gas engine working fluid compressor to work at the second speed, at which time the short-circuit solenoid valve is closed and the timing starts.

[0029] The exhaust pressure is measured in real time, and the pressure ratio is calculated in real time.

[0030] When the pressure ratio is exactly equal to the target pressure ratio, the timing stops, and the timing duration is the second duration.

[0031] In some embodiments, obtaining the second maximum torque of the hot gas engine working fluid compressor during the second performance test, and thereby calculating the second maximum power consumption of the hot gas engine working fluid compressor, specifically includes the following steps:

[0032] During the second performance test, multiple torques measured by a torque measuring instrument are obtained, and the torque with the largest value among the multiple torques is selected as the second maximum torque;

[0033] The second maximum W2 of the hot gas engine working fluid compressor is calculated using the following formula:

[0034]

[0035] Where a is a constant; T2 is the second duration; M max2 N1 is the second maximum torque; N2 is the second rotational speed.

[0036] Compared with the prior art, this application has at least one of the following beneficial effects:

[0037] 1. This application simulates the failure points that are likely to occur in the actual operation of a hot gas engine working fluid compressor by operating it under different conditions, thereby exposing potential unreliability problems and selecting qualified hot gas engine working fluid compressors for matching applications, so as to improve the reliability of the hot gas engine.

[0038] 2. The method of this application has few steps, is simple to operate and use, and can complete the performance test of the working fluid compressor. Attached Figure Description

[0039] The preferred embodiments will now be described in a clear and easy-to-understand manner, in conjunction with the accompanying drawings, to further explain the above-mentioned characteristics, technical features, advantages, and implementation methods of this application.

[0040] Figure 1 A simplified structural diagram of a performance testing system for a hot gas engine working fluid compressor provided in this application;

[0041] Figure 2 A flowchart of the first performance test in one embodiment of the test method provided in this application;

[0042] Figure 3 A flowchart of the second performance test in one embodiment of the test method provided in this application;

[0043] Figure 4 A flowchart of the first performance test in another embodiment of the test method provided in this application;

[0044] Figure 5 A flowchart of the second performance test in another embodiment of the test method provided in this application. Detailed Implementation

[0045] In the following description, specific details such as particular module structures and techniques are set forth for illustrative purposes and not for limitation, in order to provide a thorough understanding of the embodiments of this application. However, those skilled in the art will understand that this application can also be implemented in other embodiments without these specific details. In other instances, detailed descriptions of well-known modules, devices, circuits, and methods are omitted so as not to obscure the description of this application with unnecessary detail.

[0046] It should be understood that, when used in this specification and the appended claims, the term "comprising" indicates the presence of the described features, integrals, steps, operations, elements and / or components, but does not exclude the presence or addition of one or more other features, integrals, steps, operations, elements, components and / or sets.

[0047] To keep the drawings concise, each figure only schematically shows the parts relevant to the invention, and these do not represent the actual structure of the product. Furthermore, to facilitate understanding, in some figures, only one of components with the same structure or function is schematically depicted, or only one is labeled. In this document, "one" not only means "only one," but can also mean "more than one."

[0048] It should also be further understood that the term “and / or” as used in this application specification and the appended claims means any combination of one or more of the associated listed items and all possible combinations, and includes such combinations.

[0049] In this document, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "linking" should be interpreted broadly. For example, they can refer to fixed connections, detachable connections, or integral connections; they can refer to mechanical connections or electrical connections; they can refer to direct connections or indirect connections through an intermediate medium; and they can refer to the internal connection between two components. Those skilled in the art can understand the specific meaning of the above terms in this application based on the specific circumstances.

[0050] Furthermore, in the description of this application, the terms "first," "second," etc., are used only to distinguish descriptions and should not be construed as indicating or implying relative importance.

[0051] To more clearly illustrate the technical solutions in the embodiments of this application or the prior art, the specific implementation methods of this application will be described below with reference to the accompanying drawings. Obviously, the accompanying drawings described below are only some embodiments of this application. For those skilled in the art, other drawings and other implementation methods can be obtained based on these drawings without creative effort.

[0052] Reference manual attached Figure 1 An embodiment of a performance testing system for a hot gas engine working fluid compressor provided in this application includes: a main control module 10, a working fluid control module 20, a hot gas engine working fluid compressor 30, and a drive module 40.

[0053] The main control module 10 is connected to the working fluid control module 20, the hot gas engine working fluid compressor 30 and the drive module 40 respectively, and is used to control the working status of each module.

[0054] For details, please refer to the instruction manual appendix. Figure 1 , Figure 1 This is a simplified structural diagram of a performance testing system for a hot gas engine working fluid compressor provided in this application. The diagram shows the connection relationships between the various modules. The main control module 10 is wirelessly connected to the working fluid control module 20, the hot gas engine working fluid compressor 30, and the drive module 40, and can also be connected via wired connection.

[0055] Preferably, the main control module is directly connected to the exhaust solenoid valve, short-circuit solenoid valve, intake solenoid valve, drive module, first pressure sensor, second pressure sensor, and torque measuring instrument. The main control module is used to acquire the pressure of the high-pressure working fluid cylinder, the pressure, speed, and torque of the hot gas compressor working fluid, respectively, through the first pressure sensor, second pressure sensor, and torque measuring instrument, according to the sampling period. The main control module is also used to control the exhaust solenoid valve, short-circuit solenoid valve, intake solenoid valve, and drive module to operate or stop based on the operating status of the working fluid compressor performance testing module.

[0056] The working fluid control module 20 is connected to the hot gas compressor 30 and is used to receive the high-pressure working fluid compressed by the hot gas compressor and input the low-pressure working fluid into the hot gas compressor. It includes an exhaust solenoid valve 22, a high-pressure working fluid bottle 23, an overflow valve 25, a low-pressure working fluid bottle 26, and an intake solenoid valve 27 connected in sequence. It also includes a short-circuit solenoid valve 21.

[0057] Specifically, the working fluid control module includes an overflow valve, a first pressure sensor, a high-pressure working fluid cylinder, an exhaust solenoid valve, a short-circuit solenoid valve, an intake solenoid valve, a second pressure sensor, and a low-pressure working fluid cylinder. One end of the exhaust solenoid valve is connected to the working fluid exhaust port of the hot air compressor, and the other end is connected to the high-pressure working fluid cylinder. A first pressure sensor is installed between the high-pressure working fluid cylinder and the overflow valve to measure the pressure of the high-pressure working fluid cylinder. The overflow valve is also connected to the low-pressure working fluid cylinder, which is connected to the intake solenoid valve. The intake solenoid valve is connected to the working fluid inlet of the hot air compressor. A second pressure sensor is installed on the pipeline connecting the intake solenoid valve and the working fluid inlet of the hot air compressor. The two ends of the short-circuit solenoid valve are connected to the working fluid inlet and exhaust port of the hot air compressor, respectively. The connecting rod of the hot air compressor is connected to the drive module. A torque measuring instrument is installed between the hot air compressor and the drive module to measure the speed and torque. The hot gas refrigerant compressor consists of a connecting rod, piston assembly, compression chamber, and guide cylinder. The hot gas refrigerant compressor also has an oil observation port. If oil is observed in the compressor chamber through this port, it indicates an abnormality in the compressor and suggests an incomplete seal. Under normal circumstances, there should be no oil in the compressor chamber seal. In some embodiments, monitoring the oil level is used as a standard for performance testing of the hot gas refrigerant compressor.

[0058] The hot gas compressor 30 is used to pressurize the working fluid in the low-pressure working fluid bottle and allow it to enter the high-pressure working fluid bottle. It includes an inlet and an outlet; the inlet is connected to the inlet solenoid valve, and the outlet is connected to the outlet solenoid valve.

[0059] The drive module 40 is connected to the hot gas compressor 30 and is used to provide power for the compression cycle of the hot gas compressor. The drive module 40 includes a torque measuring instrument 41, which is used to measure the speed and torque of the hot gas compressor.

[0060] Specifically, the drive module simulates the crankshaft motion of a hot air engine, receives control commands from the main control module, and drives the connecting rod of the hot air engine's working fluid compressor to reciprocate. When the main control module closes the short-circuit solenoid valve, it achieves the working fluid gas pressurization function. At this time, the hot air engine's working fluid compressor pressurizes the gas in the low-pressure working fluid cylinder and sends it into the high-pressure working fluid cylinder. When the pressure in the high-pressure working fluid cylinder exceeds the overflow valve's set value, its gas automatically enters the low-pressure working fluid cylinder. The first pressure sensor measures the pressure in the high-pressure working fluid cylinder, i.e., the exhaust pressure; the second pressure sensor measures the pressure in the low-pressure working fluid cylinder, i.e., the intake pressure. The pressure ratio is defined as: exhaust pressure / intake pressure.

[0061] In this embodiment, the working fluid control module further includes a first pressure sensor 24 and a second pressure sensor 28.

[0062] One end of the first pressure sensor 24 is connected to the branch line connecting the high-pressure working fluid bottle and the overflow valve. The first pressure sensor is used to measure the discharge pressure of the hot gas engine working fluid compressor.

[0063] One end of the second pressure sensor 28 is connected to the branch line where the intake solenoid valve connects to the intake port. The second pressure sensor is used to measure the intake pressure of the working fluid compressor of the hot air engine.

[0064] The main control module 10 is also used to collect real-time data from each module in each sampling period according to a preset sampling period, and send the real-time data to the background.

[0065] The real-time data includes: the exhaust pressure measured by the first pressure sensor 24, the intake pressure obtained by the second pressure sensor 28, and the rotational speed and torque measured by the torque measuring instrument 41.

[0066] The main control module is also used to control the working time and related working parameters of the exhaust solenoid valve 22, the intake solenoid valve 27, the short-circuit solenoid valve 21 and the drive module 40.

[0067] Specifically, if the main control module controls the exhaust solenoid valve to open, the hot gas compressor is connected to the high-pressure working fluid cylinder; if it controls the exhaust solenoid valve to close, the hot gas compressor is isolated from the high-pressure working fluid cylinder. If the main control module controls the intake solenoid valve to open, the hot gas compressor is connected to the low-pressure working fluid cylinder; if it controls the intake solenoid valve to close, the hot gas compressor is isolated from the low-pressure working fluid cylinder. If the main control module controls the short-circuit solenoid valve to open, the working fluid inlet and outlet of the hot gas compressor are connected, meaning the inlet and outlet pressures are the same when the hot gas compressor is working, and the hot gas compressor cannot pressurize the working fluid gas at this time. When the main control module controls the short-circuit solenoid valve to close, the working fluid inlet and outlet of the hot gas compressor are isolated, creating a pressure ratio, and the hot gas compressor pressurizes the working fluid gas at this time.

[0068] In this embodiment, the main control module includes a frequency converter and a drive motor. The main control module issues control commands, and the frequency converter, upon receiving them, controls the drive motor to operate, thereby driving the piston assembly of the working gas compressor to reciprocate. When the main control module controls the short-circuit solenoid valve to close, the working gas pressurization function is achieved. If the connecting rod, piston assembly, compression chamber, and guide cylinder of the hot gas compressor are abnormal, the measured maximum power consumption, pressure ratio, and pressure ratio time will all be abnormal. Therefore, it can simulate the failure points that are likely to occur during the operation of the hot gas compressor, expose potential unreliable problems in the working process, and facilitate timely rectification. In addition, the present invention has few test steps, is simple to operate, and can complete the performance test of the hot gas compressor during operation.

[0069] The main control module is also used to control the short-circuit solenoid valve to be in the open state when the hot gas engine working fluid compressor is subjected to the first performance test; and to control the short-circuit solenoid valve to be in the closed state when the hot gas engine working fluid compressor is subjected to the second performance test; the main control module is also used to calculate the maximum power consumption of the hot gas engine working fluid compressor during the test.

[0070] In embodiments of this application, the working fluid compressor performance testing system further includes:

[0071] The cooling module 50 is used to cool and dissipate heat from the working fluid compressor of the hot gas engine.

[0072] The oil module 60 is used to lubricate the working fluid compressor of the hot air engine.

[0073] Specifically, a hot air compressor uses a working gas to drive a piston, offering advantages such as simple structure, low vibration and noise, and strong adaptability. In hot air compressor power generation applications, working gas pressure regulation is one of the technical means of power control. When the power of the hot air compressor increases, the working gas pressure needs to be increased; when the power decreases, the working gas pressure needs to be decreased. The cooling module is used to cool the hot air compressor's working gas compressor, keeping the equipment at a lower temperature. This effectively reduces the temperature of the mechanical equipment, improves its efficiency, reduces damage, and extends its service life. The oil module provides lubrication for the moving parts of the hot air compressor's working gas compressor. The performance of the hot air compressor's working gas compressor can also be judged by observing the remaining oil level. An observation hole is provided on the side wall of the hot air compressor's working gas compressor. If oil is observed in the compressor cavity through the observation hole, it indicates an abnormality in the hot air compressor's working gas compressor, suggesting an incompletely sealed structure. Under normal circumstances, there should be no oil in the sealed cavity of the hot air compressor's working gas compressor. In some embodiments, monitoring the remaining oil level is also used as a standard for testing the performance of the hot air compressor's working gas compressor.

[0074] In another embodiment of this invention, the main control module 10 is further configured to perform the following method: after both the first performance test and the second performance test of the hot air engine working fluid compressor are passed, the oil observation hole of the hot air engine working fluid compressor is observed to determine whether there is oil present. If the first performance test and the second performance test of the hot air engine working fluid compressor are passed, and there is no oil present in the compressor cavity after the test, it indicates that the working fluid compressor is qualified and can be used in hot air engine products.

[0075] Based on the same technical concept, this application also discloses a performance testing method for a hot gas compressor. This method can be implemented using any of the above-mentioned hot gas compressor performance testing system embodiments to test the performance of the hot gas compressor. Specifically, an embodiment of the hot gas compressor performance testing method of this application includes:

[0076] S100, Perform the first performance test on the hot gas engine working fluid compressor, as per the attached instruction manual. Figure 2 As shown: S110, control the short-circuit solenoid valve to open, and control the hot gas compressor to start running for a first duration under the first intake pressure and first speed. S120, obtain the first maximum torque of the hot gas compressor during the first performance test. S130, thereby calculating the first maximum power consumption of the hot gas compressor. S140, if the first maximum power consumption is less than the first target power consumption, S150, then the first performance test of the hot gas compressor is qualified.

[0077] Specifically, Figure 2A flowchart of the first performance test in one embodiment of the test method provided in this application is shown. The main control module controls the exhaust solenoid valve to close and the intake solenoid valve to open. When the working gas pressure of the hot gas compressor is detected to be P1, the intake solenoid valve is closed, the short-circuit solenoid valve is opened, and the drive module is controlled to drive the hot gas compressor to work at speed N1. After running for time T1, the drive module stops working. During this period, the maximum torque M is sampled and calculated. max1 Through maximum torque M max1 To calculate the maximum power consumption W1 of the working fluid compressor of the hot gas engine.

[0078] Ideally, for better testing results, the first performance test should be repeated multiple times. The number of tests depends on the actual situation, but is generally set to three times. If the maximum power consumption W1 calculated in all three tests is less than the set value of the first target power consumption, then the first performance test of the hot gas engine working fluid compressor is qualified. Alternatively, more repetitions of the first performance test can be performed.

[0079] S200, Perform a second performance test on the hot gas engine working fluid compressor, as per the attached instruction manual. Figure 3 As shown: S210, control the short-circuit solenoid valve to close, and control the hot gas compressor to operate under the second intake pressure and second speed. S220, calculate the second time taken for the pressure ratio of the hot gas compressor to increase from 1 to the target pressure ratio during the second performance test. S230, obtain the second maximum torque of the hot gas compressor during the second performance test. S240, thereby calculate the second maximum power consumption of the hot gas compressor. S250, if the second maximum power consumption is less than the second target power consumption, and the second time is less than the second target time, S260, then the second performance test of the hot gas compressor is qualified.

[0080] Specifically, Figure 3This is a flowchart of the second performance test in one embodiment of the test method provided in this application. The main control module controls the opening of the exhaust solenoid valve and the intake solenoid valve, making the pressures of the high-pressure working fluid bottle, the hot air compressor, and the low-pressure working fluid bottle the same, i.e., both the first and second pressure sensors are P2. The control drive module drives the hot air compressor to operate at N2 speed, closes the short-circuit solenoid valve, and starts timing. At this time, the initial pressure ratio of the hot air compressor is 1. The hot air compressor pressurizes the gas in the low-pressure working fluid bottle and directs it into the high-pressure working fluid bottle. When the pressure in the high-pressure working fluid bottle exceeds the overflow valve's set value, its gas automatically enters the low-pressure working fluid bottle. The first pressure sensor measures the pressure of the high-pressure working fluid bottle, i.e., the exhaust pressure; the second pressure sensor measures the pressure of the low-pressure working fluid bottle, i.e., the intake pressure. The pressure ratio is defined as exhaust pressure / intake pressure. When the pressure ratio ≥ K1, the short-circuit solenoid valve opens and timing stops. The main control module calculates the time T2 between the closing and opening of the short-circuit solenoid valve, and the maximum torque M during this period. max2 Through the maximum torque M max2 Calculate the second maximum power consumption W2 of the hot gas engine working fluid compressor. If W2 is less than the set value of the second target power consumption and T2 is less than the set time value, then the second performance test of the hot gas engine working fluid compressor is qualified.

[0081] During step S200, the main control module controls the exhaust solenoid valve and the intake solenoid valve to open. If the pressure P2 is greater than the set value, an exhaust operation is required to bring the pressure P2 to the set value. If the pressure P2 is less than the set value, an air replenishment operation is required to bring the pressure P2 to the set value before proceeding to the next step.

[0082] In another embodiment of this example, after steps S100 and S200, the working fluid compressor performance testing method further includes:

[0083] S300, Perform an oil test on the working fluid compressor of the hot gas engine.

[0084] Specifically, this includes: S310, observing the presence of engine oil inside the hot gas refrigerant compressor through an oil level observation hole installed on the compressor. If engine oil is observed in the compressor cavity through the observation hole, it indicates an abnormality in the hot gas refrigerant compressor, suggesting an incompletely sealed structure. Under normal circumstances, there should be no engine oil in the sealed cavity of the hot gas refrigerant compressor. In this embodiment, monitoring the remaining oil level is used as the third standard for testing the performance of the hot gas refrigerant compressor.

[0085] S320, if there is no engine oil, then the engine oil test of the hot gas engine working fluid compressor is qualified.

[0086] Specifically, in this embodiment, if the first performance test, the second performance test, and the oil test of the hot gas refrigerant compressor are all qualified, then the refrigerant compressor is qualified.

[0087] Another embodiment of the performance testing method for a hot gas engine working fluid compressor provided in this application is based on the above-described method embodiment, as shown in the appendix to the specification. Figure 4 As shown, the step of obtaining the first maximum torque of the hot gas engine working fluid compressor during the first performance test, and then calculating the first maximum power consumption of the hot gas engine working fluid compressor, specifically includes the following steps:

[0088] Multiple torques measured by a torque measuring instrument during the first performance test are obtained, and the torque with the largest value among the multiple torques is selected as the first maximum torque.

[0089] The first maximum power consumption W1 of the working fluid compressor of the hot gas engine is calculated using the following formula:

[0090]

[0091] Where a is a constant, T1 is the first duration, Mmax1 is the first maximum torque, and N1 is the first rotational speed.

[0092] For example, in this embodiment, the first performance test is performed three times. In the specific implementation process, the test data is as follows:

[0093] In the first performance test, the working fluid compressor of the hot air engine was set with a working fluid pressure of 3 MPa (P1), a speed of 1000 rpm (N1), and a running time of 600 seconds (T1). During this period, the main control module sampled and calculated the maximum torque M. max1 Given a value of 35 N·m, and a constant 'a' in the formula being 9550, the maximum power consumption for the first performance test is calculated as follows:

[0094] W 1(1) =600*1000*35 / 9550=2199

[0095] In the second performance test, the working fluid compressor of the hot air engine was set with a working fluid pressure of 3 MPa (P1), a speed of 1000 rpm (N1), and a running time of 600 seconds (T1). During this period, the main control module sampled and calculated the maximum torque M. max1 If the value is 34 N·m, then the maximum power consumption in the first performance test is:

[0096] W 1(2) =600*1000*34 / 9550=2136

[0097] In the third performance test, the working fluid compressor of the hot air engine was set with a working fluid pressure of 3 MPa (P1), a speed of 1000 rpm (N1), and a running time of 600 seconds (T1). During this period, the main control module sampled and calculated the maximum torque M. max1 If the value is 36 N·m, then the maximum power consumption in the first performance test is:

[0098] W 1(3) =600*1000*36 / 9550=2162

[0099] In this embodiment, the first target power consumption setting value for the first performance test is 2200. The maximum power consumption values ​​of the three first performance tests are 2199, 2136, and 2162, respectively, which are all less than 2200. Therefore, it is determined that the first performance test of the hot gas engine working fluid compressor is qualified.

[0100] Another embodiment of the performance testing method for a hot gas engine working fluid compressor provided in this application further includes the following steps, based on the above-described method embodiment:

[0101] The pressure of the high-pressure working fluid bottle, i.e., the exhaust pressure, is measured using the first pressure sensor. The pressure of the low-pressure working fluid bottle, i.e., the intake pressure, is measured using the second pressure sensor.

[0102] The pressure ratio is equal to the exhaust pressure divided by the intake pressure.

[0103] The calculation of the second time consumed during the second performance test, in which the pressure ratio of the hot gas engine working fluid compressor increases from 1 to the target pressure ratio, specifically includes the following steps:

[0104] The exhaust solenoid valve and intake solenoid valve are opened to ensure that the exhaust pressure and intake pressure are the same, both being the second intake pressure. The control drive module drives the hot gas engine working fluid compressor to operate at the second speed. At this time, the short-circuit solenoid valve is closed and timing begins.

[0105] The exhaust pressure is measured in real time, and the pressure ratio is calculated in real time.

[0106] When the pressure ratio is exactly equal to the target pressure ratio, the timing stops, and the timing duration is the second duration.

[0107] Another embodiment of this example is shown in the appendix to the specification. Figure 5 As shown, the step of obtaining the second maximum torque of the hot gas engine working fluid compressor during the second performance test, and thereby calculating the second maximum power consumption of the hot gas engine working fluid compressor, specifically includes the following steps:

[0108] During the second performance test, multiple torques measured by a torque measuring instrument are obtained, and the torque with the largest value among the multiple torques is selected as the second maximum torque.

[0109] The second maximum power consumption W2 of the working fluid compressor of the hot gas engine is calculated using the following formula:

[0110]

[0111] Where a is a constant. T2 is the second duration. M max2 N2 is the second maximum torque. N2 is the second rotational speed.

[0112] For example, in a specific implementation, in the second performance test, the second target power consumption is set to 1900, the target pressure ratio is set to K1 to 6, the time T2 between the closing and opening of the short-circuit solenoid valve is 250 seconds, the working fluid pressure of the hot air engine working fluid compressor is set to P2 to 5.8 MPa, and the rotational speed N2 is 1600 rpm. In the second performance test, when the pressure ratio is ≥6, the short-circuit solenoid valve opens and the timing stops. The main control module calculates that the time T2 between the closing and opening of the short-circuit solenoid valve is 240 seconds, and the maximum torque M during this period. max2 If the value is 46 N·m, then the maximum power consumption in the first performance test is:

[0113] W2=240*46*1600 / 9550=1850<1900

[0114] Meanwhile, T2 = 240 < 250.

[0115] The second performance test of the hot air engine working fluid compressor is qualified.

[0116] The performance testing system and method for a hot gas engine working fluid compressor of this application have the same technical concept, and the technical details of the embodiments of the two are applicable to each other. In order to reduce repetition, they will not be repeated here.

[0117] This application is described with reference to flowchart illustrations and / or block diagrams of methods, apparatus (modules), and computer program products according to embodiments of this application. It will be understood that each block of the flowchart illustrations and / or block diagrams, and combinations of blocks in the flowchart illustrations and / or block diagrams, can be implemented by computer program instructions. These computer program instructions can be provided to a processor of a general-purpose computer, special-purpose computer, embedded processor, or other programmable data processing apparatus to produce a machine, such that the instructions, which execute via the processor of the computer or other programmable data processing apparatus, generate instructions for implementing the process. Figure 1 One or more processes and / or boxes Figure 1 A device that provides the functions specified in one or more boxes.

[0118] Although preferred embodiments of this application have been described, those skilled in the art, upon learning the basic inventive concept, can make other changes and modifications to these embodiments. Therefore, the appended claims are intended to be interpreted as including the preferred embodiments as well as all changes and modifications falling within the scope of this application.

[0119] Obviously, those skilled in the art can make various modifications and variations to this application without departing from the spirit and scope of this application. Therefore, if such modifications and variations fall within the scope of the claims of this application and their equivalents, this application also intends to include such modifications and variations.

Claims

1. A heat engine working fluid compressor performance test system, characterized by, Comprise: The total control module, the working medium control module, the hot air engine working medium compressor, the driving module, the cooling module, the oil module; The working medium control module is connected with the hot air engine working medium compressor, and is used for receiving high-pressure working medium compressed by the hot air engine working medium compressor and inputting low-pressure working medium to the hot air engine working medium compressor; comprising a discharge electromagnetic valve, a high-pressure working medium bottle, an overflow valve, a low-pressure working medium bottle and an intake electromagnetic valve connected in sequence; further comprising a short circuit electromagnetic valve, a first pressure sensor and a second pressure sensor; The hot air engine working medium compressor is used for pressurizing the working medium of the low-pressure working medium bottle and making it enter the high-pressure working medium bottle; comprising an air inlet and an air outlet, the air inlet is connected with the intake electromagnetic valve; the air outlet is connected with the discharge electromagnetic valve; One end of the first pressure sensor is connected on the branch connected between the high-pressure working medium bottle and the overflow valve; the first pressure sensor is used for measuring the exhaust pressure of the hot air engine working medium compressor; One end of the second pressure sensor is connected on the branch connected between the intake electromagnetic valve and the air inlet; the second pressure sensor is used for measuring the intake pressure of the hot air engine working medium compressor; The driving module is connected with the hot air engine working medium compressor, and is used for providing power for the compression cycle of the hot air engine working medium compressor; the driving module comprises a torque measuring instrument, and the torque measuring instrument is used for measuring the rotating speed and the torque of the hot air engine working medium compressor; The total control module is connected with the remaining modules respectively, and is used for controlling the working state of each module, collecting real-time data of each module in each sampling period according to a preset sampling period, and sending the real-time data to the background; the real-time data comprises the exhaust pressure measured by the first pressure sensor, the intake pressure obtained by the second pressure sensor, and the rotating speed and the torque measured by the torque measuring instrument; The total control module is also used for controlling the working time of the discharge electromagnetic valve, the intake electromagnetic valve, the short circuit electromagnetic valve and the driving module; The total control module is also used for controlling the short circuit electromagnetic valve to be in an open state when the hot air engine working medium compressor is tested for the first performance, and controlling the short circuit electromagnetic valve to be in a closed state when the hot air engine working medium compressor is tested for the second performance; the total control module is also used for calculating the maximum power consumption of the hot air engine working medium compressor in the testing process; The cooling module is used for cooling and dissipating heat of the hot air engine working medium compressor; The oil module is used for lubricating the hot air engine working medium compressor.

2. A method of testing the performance of a hot gas engine working fluid compressor, characterized by, The test method is suitable for the hot air engine working medium compressor performance test system in claim 1, and comprises the following steps: The first performance test of the heat engine working substance compressor is carried out: the short circuit electromagnetic valve is controlled to be opened, the heat engine working substance compressor is controlled to run for a first time length under a first inlet pressure and a first rotating speed, a first maximum torque of the heat engine working substance compressor in the first performance test is obtained, and a first maximum power consumption of the heat engine working substance compressor is calculated; if the first maximum power consumption is less than a first target power consumption, the first performance test of the heat engine working substance compressor is qualified. The second performance test of the heat engine working substance compressor is carried out: the short circuit electromagnetic valve is controlled to be closed, the heat engine working substance compressor is controlled to run under a second inlet pressure and a second rotating speed, a second time length consumed by the heat engine working substance compressor in a process in which a pressure ratio is increased from 1 to a target pressure ratio is calculated, a second maximum torque of the heat engine working substance compressor in the second performance test is obtained, and a second maximum power consumption of the heat engine working substance compressor is calculated; if the second maximum power consumption is less than a second target power consumption and the second time length is less than a second target time length, the second performance test of the heat engine working substance compressor is qualified.

3. A method of testing the performance of a hot gas engine working fluid compressor as defined in claim 2, wherein, The first maximum torque of the heat engine working substance compressor in the first performance test is obtained, and the first maximum power consumption of the heat engine working substance compressor is calculated, and the method specifically comprises the following steps: a maximum torque in the multiple torques is selected as the first maximum torque; the first maximum power consumption W1 of the heat engine working substance compressor is calculated through the following formula: ； wherein a is a constant; T1 is the first time length; M max1 is the first maximum torque; and N1 is the first rotational speed.

4. A method of testing the performance of a hot gas engine working fluid compressor as defined in claim 2, wherein, The following steps are further included: a high-pressure working substance bottle pressure, i.e., an exhaust pressure, is measured by the first pressure sensor, and a low-pressure working substance bottle pressure, i.e., an inlet pressure, is measured by the second pressure sensor; the pressure ratio = the exhaust pressure / inlet pressure.

5. A method of testing the performance of a hot gas engine working fluid compressor as defined in claim 2, wherein, The second time length consumed by the heat engine working substance compressor in the process in which the pressure ratio is increased from 1 to the target pressure ratio in the second performance test is calculated, and the method specifically comprises the following steps: the exhaust electromagnetic valve and the inlet electromagnetic valve are controlled to be opened, the exhaust pressure and the inlet pressure are controlled to be the same and to be the second inlet pressure, the driving module is controlled to drive the heat engine working substance compressor to work at the second rotating speed, the short circuit electromagnetic valve is closed at this time, and timing is started; the exhaust pressure is measured in real time, and the pressure ratio is calculated in real time; when the pressure ratio is equal to the target pressure ratio, the timing is stopped, and the time of the timing is the second time length.

6. A method of testing the performance of a hot gas engine working substance compressor as described in claim 2, wherein, The second maximum torque of the heat engine working substance compressor in the second performance test is obtained, and the second maximum power consumption of the heat engine working substance compressor is calculated, and the method specifically comprises the following steps: a maximum torque in the multiple torques is selected as the second maximum torque; the second maximum power consumption W2 of the heat engine working substance compressor is calculated through the following formula: ； wherein a is a constant; T2 is the second time length; M max2 is the second maximum torque; N2 is the second rotational speed.

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